CN217226825U - Master cylinder hydraulic system of large-tonnage hydraulic press - Google Patents
Master cylinder hydraulic system of large-tonnage hydraulic press Download PDFInfo
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- CN217226825U CN217226825U CN202220646041.8U CN202220646041U CN217226825U CN 217226825 U CN217226825 U CN 217226825U CN 202220646041 U CN202220646041 U CN 202220646041U CN 217226825 U CN217226825 U CN 217226825U
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Abstract
The utility model discloses a master cylinder hydraulic system of large-tonnage hydraulic press, the last hydraulic fluid port of each group master cylinder links to each other with last oil tank through the prefill valve respectively, the main pressure oil circuit links to each other with cartridge valve C1's entry, cartridge valve C1's export links to each other with cartridge valve C4's entry, cartridge valve C4's export links to each other with cartridge valve C5's entry, cartridge valve C5's export links to each other with the last hydraulic fluid port of master cylinder and the B mouth of proportion overflow valve, the A mouth of proportion overflow valve connects the oil tank, the control mouth links to each other with the energy storage ware; a hydraulic control port of the cartridge valve C1 is connected with a port A of the electromagnetic directional valve YA1, a port P of the YA1 is connected with a main pressure oil way, and a port T is connected with a lower oil tank; the hydraulic control port of the cartridge valve C5 is controlled by the port A of the electromagnetic directional valve YA5 to be connected, and the port P of the YA5 is connected with the inlet of the cartridge valve C5. The system can press large-area workpieces, all the main cylinders act uniformly, and unbalance loading cannot occur.
Description
Technical Field
The utility model relates to a hydraulic press especially relates to a master cylinder hydraulic system of large-tonnage hydraulic press, belongs to hydraulic control system technical field.
Background
The hydraulic press is a device which uses liquid as a working medium and is used for transferring energy to realize various processes, and is commonly used for pressing. Traditional hydraulic press is including controlling the stand, and the top of controlling the stand passes through the entablature and links to each other, and the bottom of controlling the stand is connected with the workstation, is equipped with the slider between entablature and the workstation, and the master cylinder is installed at the center of entablature. The main cylinder drives the sliding block to move downwards to press the workpiece fixed on the workbench, so that the workpiece is deformed into a required shape.
For processing large-sized workpieces, a workbench with a large area is required, and a sliding block with a large cross section is matched with the workbench. In order to avoid stress concentration and ensure the smooth descending of the slide block, a plurality of rows and a plurality of columns of master cylinders, for example, 4 rows by 4 columns, are required to be arranged on the upper cross beam, 16 master cylinders are required in total, and the total pressure reaches more than 1 ten thousand tons. The lower ends of the plungers of the main cylinders are fixedly connected with the sliding blocks respectively, the main cylinders must act in a unified mode, the sliding blocks are driven to uniformly press the workpiece fixed on the workbench, and the unbalance loading phenomenon is avoided.
The machine tool is required to be rapidly opened by each liquid filling valve during rapid die closing and pressure building and return stroke, and is required to be rapidly closed by each liquid filling valve during pressurization, and the conventional liquid filling valves are not rapidly and unstably opened and closed, so that the situation of inconsistent actions is easy to occur.
When the sliding block releases pressure, the pressure of the main cylinder is expected to be slowly released under a controlled state, and the sliding block rebounding vibration caused by too fast pressure release is avoided.
SUMMERY OF THE UTILITY MODEL
An object of the utility model is to overcome the problem that exists among the prior art, provide a master cylinder hydraulic system of large-tonnage hydraulic press, can suppress the work piece of large tracts of land, the suppression power can reach more than ten thousand tons, and the action of each master cylinder is unified, can not take place the unbalance loading.
In order to solve the technical problem, the utility model discloses a master cylinder hydraulic system of large-tonnage hydraulic press, including the multiunit master cylinder of drive slider, the last chamber hydraulic fluid port of each group master cylinder links to each other with last oil tank through the prefill valve respectively, main pressure oil circuit G1 links to each other with the entry of cartridge valve C1, the export of cartridge valve C1 links to each other with the entry of cartridge valve C4, the export of cartridge valve C4 links to each other with master cylinder oil circuit G4, master cylinder oil circuit G4 links to each other with the entry of cartridge valve C5, the export of cartridge valve C5 links to each other with the last chamber hydraulic fluid port of a group master cylinder and the B mouth of proportional overflow valve YAA, the A mouth of proportional overflow valve YAA connects the oil tank, the control mouth of proportional overflow valve YAA links to each other with the hydraulic fluid port of energy storage ware AC 1; a hydraulic control port of the cartridge valve C1 is connected with a port A of the electromagnetic directional valve YA1, a port P of the electromagnetic directional valve YA1 is connected with a main pressure oil way G1, and a port T of the electromagnetic directional valve YA1 is connected with a lower oil tank; the hydraulic control port of the cartridge valve C5 is connected with the middle port of the shuttle valve S1, the left inlet of the shuttle valve S1 is connected with the outlet of the cartridge valve C5, the right inlet of the shuttle valve S1 is connected with the port A of the electromagnetic directional valve YA5, and the port P of the electromagnetic directional valve YA5 is connected with the inlet of the cartridge valve C5.
As an improvement of the utility model, the main pressure oil path G1 is also connected with the inlet of the cartridge valve C2, and the outlet of the cartridge valve C2 is connected with the lower oil tank; a hydraulic control port of the cartridge valve C2 is connected with a port A of the electromagnetic directional valve YA2, a port P of the electromagnetic directional valve YA2 is connected with a main pressure oil way G1, and a port T of the electromagnetic directional valve YA2 is connected with a lower oil tank; the electromagnetic directional valve YA1 and the electromagnetic directional valve YA2 are two-position four-way electromagnetic directional valves.
As a further improvement of the utility model, the outlet of the servo pump P1 is connected with the inlets of the cartridge valve C6 and the check valve D2, the outlet of the cartridge valve C6 is connected with the lower oil tank, the outlet of the check valve D2 is connected with the oil port of the energy accumulator AC1, and the oil port pipeline of the energy accumulator AC1 is provided with a pressure sensor BP 1; the hydraulic control port of the cartridge valve C6 is connected with the lower oil tank through a pressure regulating valve F1 and is connected with the port B of the electromagnetic directional valve YA6, and the port T of the electromagnetic directional valve YA6 is connected with the lower oil tank.
As a further improvement of the present invention, the line pressure oil path G1 is connected to the inlet of the cartridge valve C3, the outlet of the cartridge valve C3 is connected to the P port of the electro-hydraulic directional valve YA4 through the check valve D1, the T port of the electro-hydraulic directional valve YA4 is connected to the oil tank, the a port of the electro-hydraulic directional valve YA4 is connected to the control oil path G2 under the liquid filling valve, the B port of the electro-hydraulic directional valve YA4 is connected to the control oil path G3 on the liquid filling valve, and the electro-hydraulic directional valve YA4 is a two-position four-way electromagnetic directional valve; the lower charging valve control oil path G2 is respectively connected with the lower liquid control port of each charging valve; and the upper liquid control oil path G3 of the liquid charging valve is respectively connected with the upper liquid control port of each liquid charging valve.
As a further improvement of the present invention, the hydraulic control port of the cartridge valve C3 is connected to the port a of the electromagnetic directional valve YA3, the port P of the electromagnetic directional valve YA3 is connected to the line pressure oil path G1, the port T of the electromagnetic directional valve YA3 is connected to the lower oil tank, and the electromagnetic directional valve YA3 is a two-position four-way electromagnetic directional valve.
Compared with the prior art, the utility model discloses following beneficial effect has been obtained: 1. the adoption of the electro-hydraulic reversing valve YA4 with the DG25 drift diameter can meet and realize the active, quick, stable and reliable opening and closing of each prefill valve, can improve the response time of opening or closing the prefill valve, realize the unified quick opening and quick pressure build of a plurality of prefill valves and reduce the eddy current noise;
2. the main cylinder adopts a mode of uniformly distributing a plurality of groups, so that the problems of large machine tool table surface and concentrated machine body stress are solved; the master cylinders are in a group, the pressure groups are independently arranged, and the master cylinders can be respectively adjusted according to the density requirement of parts, so that the yield of products is improved.
3. The pressure relief of the main cylinder is gentle, the internal stress generated after the product is pressed by large tonnage is absorbed, and the rebound vibration of the sliding block is avoided.
Drawings
The invention will be described in further detail with reference to the drawings and the detailed description, which are provided for reference and illustration purposes only and are not intended to limit the invention.
FIG. 1 is a hydraulic schematic diagram of a main cylinder hydraulic system of the large-tonnage hydraulic press of the present invention.
Detailed Description
As shown in figure 1, the main cylinder hydraulic system of the large-tonnage hydraulic machine comprises a plurality of groups of main cylinders for driving the sliding block, and upper cavity oil ports of the main cylinders are respectively connected with an upper oil tank through liquid filling valves. Taking one group of four master cylinders as an example, the upper cavity oil port of each master cylinder is respectively connected with the upper oil tank through a charging valve CF1, a charging valve CF2, a charging valve CF3 and a charging valve CF 4.
The main pressure oil path G1 is connected with an inlet of a cartridge valve C1, an outlet of the cartridge valve C1 is connected with an inlet of the cartridge valve C4, an outlet of the cartridge valve C4 is connected with a main cylinder oil path G4, a main cylinder oil path G4 is connected with an inlet of the cartridge valve C5, an outlet of the cartridge valve C5 is connected with upper cavity oil ports of a group of main cylinders and a B port of a proportional overflow valve YAA, an A port of the proportional overflow valve YAA is connected with an oil tank, and a control port of the proportional overflow valve YAA is connected with an oil port of an energy accumulator AC 1.
A hydraulic control port of the cartridge valve C1 is connected with a port A of the electromagnetic directional valve YA1, a port P of the electromagnetic directional valve YA1 is connected with a main pressure oil way G1, and a port T of the electromagnetic directional valve YA1 is connected with a lower oil tank;
the pilot control port of the cartridge valve C5 is connected with the middle port of the shuttle valve S1, the left inlet of the shuttle valve S1 is connected with the outlet of the cartridge valve C5, the right inlet of the shuttle valve S1 is connected with the port A of the electromagnetic directional valve YA5, and the port P of the electromagnetic directional valve YA5 is connected with the inlet of the cartridge valve C5.
The main pressure oil path G1 is also connected with the inlet of the cartridge valve C2, and the outlet of the cartridge valve C2 is connected with the lower oil tank; a hydraulic control port of the cartridge valve C2 is connected with a port A of the electromagnetic directional valve YA2, a port P of the electromagnetic directional valve YA2 is connected with a main pressure oil path G1, and a port T of the electromagnetic directional valve YA2 is connected with a lower oil tank; the electromagnetic directional valve YA1 and the electromagnetic directional valve YA2 are two-position four-way electromagnetic directional valves.
An outlet of the servo pump P1 is connected with inlets of a cartridge valve C6 and a check valve D2, an outlet of the cartridge valve C6 is connected with a lower oil tank, an outlet of the check valve D2 is connected with an oil port of an energy accumulator AC1, and a pressure sensor BP1 is installed on an oil port pipeline of the energy accumulator AC 1; the hydraulic control port of the cartridge valve C6 is connected with the lower oil tank through a pressure regulating valve F1 and is connected with the port B of the electromagnetic directional valve YA6, and the port T of the electromagnetic directional valve YA6 is connected with the lower oil tank.
The main pressure oil way G1 is connected with an inlet of a cartridge valve C3, an outlet of the cartridge valve C3 is connected with a P port of an electro-hydraulic reversing valve YA4 through a one-way valve D1, a T port of the electro-hydraulic reversing valve YA4 is connected with an oil tank, an A port of the electro-hydraulic reversing valve YA4 is connected with a lower control oil way G2 of a liquid charging valve, a B port of the electro-hydraulic reversing valve YA4 is connected with an upper control oil way G3 of the liquid charging valve, and the electro-hydraulic reversing valve YA4 is a two-position four-way electromagnetic reversing valve; a lower liquid filling valve control oil path G2 is respectively connected with lower liquid control ports of the liquid filling valves; and the upper control oil path G3 of the liquid filling valve is respectively connected with the upper liquid control port of each liquid filling valve.
A hydraulic control port of the cartridge valve C3 is connected with a port A of an electromagnetic directional valve YA3, a port P of the electromagnetic directional valve YA3 is connected with a main pressure oil way G1, a port T of the electromagnetic directional valve YA3 is connected with a lower oil tank, and the electromagnetic directional valve YA3 is a two-position four-way electromagnetic directional valve.
When the slide block is quickly lowered, the electromagnetic reversing valve YA2 is de-energized, the hydraulic control port of the cartridge valve C2 builds pressure and is closed, and the main pressure oil path G1 builds pressure;
when the electromagnetic directional valve YA5 is electrified, the cartridge valve C5 is opened, and the pressure oil in the main cylinder oil way G4 enters the upper cavities of the four main cylinders;
the electromagnetic reversing valve YA3 is electrified, the cartridge valve C3 is opened, oil is supplied to a port P of the electro-hydraulic reversing valve YA4, and the pressure regulating valve F2 controls the oil pressure of the port P of the electro-hydraulic reversing valve YA4 to be 15 MPa;
the electro-hydraulic reversing valve YA4 is electrified, a port P is communicated with a port B, a port A is communicated with a port T, a lower control oil path G2 of the charging valve releases pressure, an upper control oil path G3 of the charging valve builds pressure, an upper liquid control port of each charging valve builds pressure, and all the charging valves are opened actively; the oil in the oil feeding tank is quickly fed into the upper cavities of the main cylinders.
When the slide block slowly descends, the electro-hydraulic reversing valve YA4 is de-energized, the port P is communicated with the port A, the port B is communicated with the port T, the lower control oil path G2 of the liquid charging valve builds pressure, the lower control ports of all the liquid charging valves build pressure, the upper control oil path G3 of the liquid charging valve releases pressure, and all the liquid charging valves are actively closed.
The drift diameters of the lower control oil path G2 of the liquid filling valve and the upper control oil path G3 of the liquid filling valve are 25mm, the control oil ports of the main cylinders are sufficiently supplied with oil, and even if the total number of the main cylinders reaches 16, synchronous opening or closing can be ensured.
When the sliding block releases pressure, the proportional relief valve YAA is electrified, the port B is communicated with the port A, the upper cavities of the four main cylinders are controlled by the proportional relief valve YAA to release pressure slowly to a lower oil tank, so that the internal stress generated after a product is pressed by large tonnage is absorbed, and the sliding block is prevented from rebounding and vibrating due to too fast pressure release; the accumulator AC1 keeps the control oil ports of the proportional relief valves constant.
The master cylinder oil passage G4 also supplies oil to the control oil passages of other groups of master cylinders, and the control principle is the same as above.
The servo pump P1 can be always kept in an operating state, when the pressure of the control oil path of the proportional relief valve YAA is lower than a set value, the pressure sensor BP1 sends a signal, the electromagnetic directional valve YA6 is electrified, the cartridge valve C6 is closed, and the pressure oil is filled into the energy accumulator AC 1.
The above description is only a preferred embodiment of the present invention, and not intended to limit the scope of the present invention. In addition to the above embodiments, the present invention may have other embodiments. All the technical solutions formed by adopting equivalent substitutions or equivalent transformations fall within the protection scope claimed by the present invention. The undescribed technical features of the present invention can be realized by or using the prior art, and are not described herein again.
Claims (5)
1. The main cylinder hydraulic system of the large-tonnage hydraulic press comprises a plurality of groups of main cylinders for driving a sliding block, wherein upper cavity oil ports of the groups of main cylinders are respectively connected with an upper oil tank through a liquid charging valve, and the main cylinder hydraulic system is characterized in that: the main pressure oil way G1 is connected with an inlet of a cartridge valve C1, an outlet of the cartridge valve C1 is connected with an inlet of the cartridge valve C4, an outlet of the cartridge valve C4 is connected with a main cylinder oil way G4, a main cylinder oil way G4 is connected with an inlet of the cartridge valve C5, an outlet of the cartridge valve C5 is connected with upper cavity oil ports of a group of main cylinders and a B port of a proportional overflow valve YAA, an A port of the proportional overflow valve YAA is connected with an oil tank, and a control port of the proportional overflow valve YAA is connected with an oil port of an energy accumulator AC 1;
a hydraulic control port of the cartridge valve C1 is connected with a port A of the electromagnetic directional valve YA1, a port P of the electromagnetic directional valve YA1 is connected with a main pressure oil way G1, and a port T of the electromagnetic directional valve YA1 is connected with a lower oil tank;
the hydraulic control port of the cartridge valve C5 is connected with the middle port of the shuttle valve S1, the left inlet of the shuttle valve S1 is connected with the outlet of the cartridge valve C5, the right inlet of the shuttle valve S1 is connected with the port A of the electromagnetic directional valve YA5, and the port P of the electromagnetic directional valve YA5 is connected with the inlet of the cartridge valve C5.
2. The master cylinder hydraulic system of a large tonnage hydraulic machine as set forth in claim 1, characterized in that: the main pressure oil path G1 is also connected with the inlet of the cartridge valve C2, and the outlet of the cartridge valve C2 is connected with the lower oil tank; a hydraulic control port of the cartridge valve C2 is connected with a port A of the electromagnetic directional valve YA2, a port P of the electromagnetic directional valve YA2 is connected with a main pressure oil way G1, and a port T of the electromagnetic directional valve YA2 is connected with a lower oil tank; the electromagnetic directional valve YA1 and the electromagnetic directional valve YA2 are two-position four-way electromagnetic directional valves.
3. The master cylinder hydraulic system of a large tonnage hydraulic machine as set forth in claim 1, characterized in that: an outlet of the servo pump P1 is connected with inlets of a cartridge valve C6 and a check valve D2, an outlet of the cartridge valve C6 is connected with a lower oil tank, an outlet of the check valve D2 is connected with an oil port of the energy accumulator AC1, and a pressure sensor BP1 is installed on an oil port pipeline of the energy accumulator AC 1; the hydraulic control port of the cartridge valve C6 is connected with the lower oil tank through a pressure regulating valve F1 and is connected with the port B of the electromagnetic directional valve YA6, and the port T of the electromagnetic directional valve YA6 is connected with the lower oil tank.
4. The master cylinder hydraulic system of a large tonnage hydraulic machine as set forth in claim 1, characterized in that: the main pressure oil way G1 is connected with an inlet of a cartridge valve C3, an outlet of the cartridge valve C3 is connected with a P port of an electro-hydraulic reversing valve YA4 through a one-way valve D1, a T port of the electro-hydraulic reversing valve YA4 is connected with an oil tank, an A port of the electro-hydraulic reversing valve YA4 is connected with a lower control oil way G2 of a liquid charging valve, a B port of the electro-hydraulic reversing valve YA4 is connected with an upper control oil way G3 of the liquid charging valve, and the electro-hydraulic reversing valve YA4 is a two-position four-way electromagnetic reversing valve; the lower liquid charging valve control oil path G2 is respectively connected with the lower liquid charging port of each liquid charging valve; and the upper liquid control oil path G3 of the liquid charging valve is respectively connected with the upper liquid control port of each liquid charging valve.
5. The master cylinder hydraulic system of a large tonnage hydraulic machine as set forth in claim 4, characterized in that: the hydraulic control port of the cartridge valve C3 is connected with the port A of the electromagnetic directional valve YA3, the port P of the electromagnetic directional valve YA3 is connected with the main pressure oil way G1, the port T of the electromagnetic directional valve YA3 is connected with the lower oil tank, and the electromagnetic directional valve YA3 is a two-position four-way electromagnetic directional valve.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220646041.8U CN217226825U (en) | 2022-03-23 | 2022-03-23 | Master cylinder hydraulic system of large-tonnage hydraulic press |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202220646041.8U CN217226825U (en) | 2022-03-23 | 2022-03-23 | Master cylinder hydraulic system of large-tonnage hydraulic press |
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| CN217226825U true CN217226825U (en) | 2022-08-19 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202220646041.8U Active CN217226825U (en) | 2022-03-23 | 2022-03-23 | Master cylinder hydraulic system of large-tonnage hydraulic press |
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| CN (1) | CN217226825U (en) |
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